Hydraulic control apparatus



T. F. FLAVlN ET AL HYDRAULIC CONTROL APPARATUS June 5, 1962 3,03 7,689

5 Sheets-Sheet 1 Filed June 10, 1959 llVVf/Wfl/FS THEODORE F. FLAVIN HAROLD P. WICKLUND June 5, 1962 T. F. FLAVIN ET AL 3,037,689

HYDRAULIC CONTROL APPARATUS Filed June 10, 1959 5 Sheets-Sheet 2 FIG. 2

June 5, 1962 T. F. FLAVlN ET AL 3,037,689

HYDRAULIC CONTROL APPARATUS Filed June 10, 1959 5 Sheets-Sheet 3 FIG. 3

FIG. 3

IG. 3e

June 5, 1962 T. F. FLAVlN ET AL 7,

. HYDRAULIC CONTROL APPARATUS Filed June 10, 1959 5 Sheets-Sheet 4 June 5, 1962 T. F. FLAVIN ET AL HYDRAULIC CONTROL APPARATUS 5 Sheets-Sheet 5 Filed June 10,, 1959 305 m 6 853a ME; .62 .62

.2 oofon @ON llllllll-llll qlllll Ewzm imwa EB rates nite The present invention relates to hydraulic apparatus, particularly to hydraulic apparatus for rapidly moving an element at a predetermined time and then restoring the same to its initial position, and, more particularly, to apparatus for selectively controlling the passage of working fluid or hydraulic impulses.

While the instant invention may be used for general applications in the art of hydraulic apparatus, it is particularly suited for incorporation in record card punching machines of the type having the facility for selective punching. The advantages of utilizing hydraulic apparatus for selectively operating punches of the type for perforating record cards so as to attain higher speeds of operation and still retain a high degree of selective control over the punches have already been recognized.

In some arrangements of hydraulic apparatus for selectively punching record cards, the working fluid is cyclically admitted to a fluid chamber in which one or more valves are disposed for controlling the passage of fluid under pressure from the chamber to act upon a punch operator and electromagnetic means have been employed for controlling the operation of the valve mechanism for gating the working fluid pressure which actuates the punch operator or element for effecting the punching. However, it has been recognized that, if the magnetic means requires a large amount of energy in operating the control valve mechanism, then the desirable high speeds of operation cannot be attained because the magnetic means, under these conditions, is a relatively slow operating mechanism.

Accordingly, it has been the practice to provide auxiliary apparatus for cooperating with the magnetic means for operating the control valve mechanism whereby the magnetic means only exercises a control function and the auxiliary apparatus furnishes the power into the system for operating the control valve mechanism. Under this type of an arragement, the magnetic means is often referred to as a no work magnet.

The present invention is directed to achieve high-speed operation without resorting to the use of an auxiliary means for operating the control valve mechanism whose operation is controlled by magnetic means. In the invention under consideration, the working fluid itself is utilized to aid magnetic means for operating the control valve mechanism to open and closed positions. By this arrangement, the amount of energy or power required of the magnetic means in operation of the control valve mechanism is so greatly reduced that the magnetic means may operate at substantially the same high speeds as if it were a no work magnet.

Essentially, the magnetic means in the subject invention biases the control valve mechanism toward an open or closed position. The Working fluid, which is cyclically admitted to the fluid chamber wherein the control valve mechanism is situated, acts to move the control valve mechanism to the open or closed position depending upon whether the control valve mechanism is biased by the magnetic means to the open or closed position. Of course, as it will be seen shortly, the control valve mechanism may already be in its fully open or closed position at the instant the working fluid impulse is applied to the fluid chamber. In any event, a very important factor to consider when operating at very high speeds is that the cal magnetic means for controlling the valve mechanism must, in a manner of speaking, drop out the valve mechanism as well as to pick it up. The ability of the magnetic means to permit rapid opening of the valve mechanism would be of little use if the valve mechanism could not be closed just as rapidly. If the valve mechanism were not closed rapidly, the admission of fluid under pressure to the fluid chamber would have to be halted until the valve was closed. Otherwise, fluid under pressure would pass the port or outlet supposedly closed by the control valve to actuate the punch operator and effect a punching operation when the same was not to have taken place. If the fluid under pressure cannot be admitted to the fluid chamber at a high cyclic rate, then, of course, punching cannot occur at a high rate.

Hence, by utilizing the working fluid itself to aid the magnetic means in rapidly opening and closing the valve mechanism, selective punching at high cyclic rates may take place. Further, while the magnetic means is capable of moving the valve mechanism to the open and closed positions, it is only necessary that the magnetic means move the valve toward the open and closed positions because the working fluid can then be admitted, when the valve mechanism is moved by the magnetic means toward these positions, to open or close the valve.

In high-speed operation of the present invention, when the magnetic means is successively energized for two or more cycles of operation, the control valve mechanism doesnt have time to fully restore to the closed position even though the magnetic means becomes de-energized between periods of energization. Hence, under these conditions, the control valve mechanism will be substantially in the fully opened position upon admission of the Working fluid pressure impulse to the fluid chamber. On the other hand, if the magnetic means is successively caused to remain de-energized for two or more cycles of operation, the control valve mechanism will be in the closed position at the instant the working fluid pressure impulse is admitted to the fluid chamber because the control valve had been closed by the working fluid pressure upon the first instance that the magnetic means was not energized.

However, during a cycle of operation when the magnetic means is energized after a period of de-energization or is de-energized after a period of energization, the control valve mechanism will be in different intermediate positions at the instant the working fluid pressure impulse is applied to the fluid chamber. If the magnetic means is energized during a cycle of operation following a cycle during which the magnetic means was de-energized, the control valve mechanism will be biased toward the open position so that the working fluid pressure impulse will enter the fluid chamber and move the control valve mechanism to its fully opened position. Whereas, if the magnetic means is de-energized during a cycle of operation following a cycle during which the magnetic means had been energized, the control valve mechanism Will be biased toward the closed position; and, upon entry of the working fluid pressure impulse, the control valve mechanism will be moved to the closed position.

The underlying principles for utilizing the working fluid under pressure to move the control valve to the closed position when the same is biased toward the closed position by the magnetic means are different from the principles involved in utilizing the working fluid under pressure for moving the control valve to the open position when the same is biased toward the open position by the magnetic means.

When the control valve mechanism is biased toward the closed position by the magnetic means, it is in such a position that, when the working fluid pressure impulse is admitted to the fluid chamber, the fluid flows past one face of the control valve mechanism at a high velocity and thereby reduces the fluid pressure acting upon that face. The fluid pressure on that face is sufliciently less than the pressure on the other face of the valve mechanism so that the total forces involved move the control valve mechanism to the closed position and thereby cut off any further flow of fluid. The physical arrangement of the apparatus is such that the amount of working fluid passing the one face of the control valve mechanism before the same closes is negligible and may pass as leakage. However, when the control valve mechanism is biased toward the open position at the time the working fluid pressure impulse is admitted to the fluid chamber, the valve mechanism is in such a position that the fluid flowing past the one face of the control valve mechanism does not reduce the fluid pressure acting upon that face compared to the fluid pressure acting upon the other face of the control valve. However, the one face of the control valve, or the face adjacent to the outlet of the fluid chamber, is of greater area than the area of the other face. Hence, since the pressures on the faces are approximately equal in this instance, the resultant effect is that the control valve mechanism is moved to the open position.

While the area of one face of the control valve mechanism is greater than the other, this difference in area becomes relatively unimportant when the control valve is biased toward the closed position, due to the fact that the pressure acting on the larger area is much less than the pressure acting on the smaller area. However, when the control valve is biased toward the open position, this difference in area is significant because the pressure on the faces of the valve is substantially equal.

Accordingly, it is a prime object of this invention to provide an improved magnetically operated control apparatus for controlling the passage of fluid under pressure which utilizes the energy of the fluid that it controls in performing its control function.

Another very important object of this invention is to provide magnetically operated control apparatus for controlling the passage of fluid under pressure which is capable of high-speed operation.

Still another object of this invention is to provide magnetically operated control apparatus for controlling the passage of fluid under pressure which is selectively biased toward an open or closed position so that, upon application of fluid under pressure, the apparatus is moved to the open or closed position.

A further object of this invention is to provide magnetically operated control apparatus for controlling the passage of fluid under pressure which is of simple construction.

Still another very important object of the invention is to provide an improved hydraulic operating system for a record card punch wherein reciprocating strokes of the card punch are effected by fluid impulses generated at a very high cyclic rate.

Yet another object of this invention is to provide hydraulic apparatus which is selectively operable to admit fluid impulses generated at a high cyclic rate to act upon punch operators and thereby effect selective punching of discrete index positions of record cards.

An additional object of this invention is to provide electromagnetic means for selectively biasing control valve mechanism toward open and closed positions whereby fluid impulses generated at a very high cyclic rate act upon'said control valve mechanism to move the same to open and closed positions, depending upon the biased state of the control valve mechanism at the time of admission of the fluid impulses, which pass on to actuate punch operators when the control valve mechanism is moved to the open position and thereby effect selective punching of record cards.

Other objects of the invention will be pointed out in the following description and claims and illustrated in the accompanying drawings, which disclose, by way of examples, the principle of the invention and the best mode which has been contemplated by applying that principle.

In the drawings:

FIG. 1 is a view schematically showing the complete hydraulic apparatus embodying the present invention;

FIG. 2 is a perspective view showing the hydraulic control and punching apparatus;

FIGS. 3a, 3b and 3c are views schematically showing the difierent positions of the poppet control valves at the time fluid under pressure is admitted-etc the fluid chamber;

FIGS. 3d and 3e are schematic views showing pressure distribution on the faces of the poppet control valves when the same are in the positions shown in FIGS. 30 and 317, respectively;

FIG. 4 is a perspective view showing the hydraulic apparatus of the invention as incorporated in a punching machine; and,

FIG. 5 is a timing diagram showing the control operation of the hydraulic apparatus and the operation of the punches in the punching machine.

Referring to the drawings and particularly to FIG. 1, the invention is illustrated, by way of example, as an arrangement of hydraulic apparatus including a fluid pressure generating means or pump 10 driven by a motor M for supplying the working fluid under pressure cyclically admitted by valve means 20 to a fluid chamber 40.

The pump 10 withdraws fluid from a reservoir 11 through a suction conduit 12 to deliver fluid under pressure to a conduit 13. Interconnected by the conduit 13 are check valve 14 to prevent 'backflow of fluid, filter 15, fluid pressure regulator 16, and accumulator 17 to compensate for pressure fluctuations.

The conduit 13 leads on and is connected to a fluid conducting passage 21 of a cored housing 22 of the valve means 20. The housing 22 is provided with a cylindrical bore 23 open at one end and closed at the other with a central recessed port 24 intermediate of the ends to receive a reciprocatable slide or spool-type control valve 25. The spool valve 25 includes a central land 26 disposed between spaced end lands 27 and 28, respectively. The central land 26 is adapted to control fluid fiow through the related recessed port 24. Additionally, the lands of the spool valve 25 lie within the cylindrical bore 23 to provide upper and lower fluid chambers 29 and 30, respectively, disposed on opposite sides of the central land 26.

The fluid conducting passage 21, which connects with the conduit 13, also is formed to communicate with the lower fluid chamber 30. The upper fluid chamber 29 is in communication with the reservoir 11 by means of a fluid passage 31 formed in the housing 22 to connect with a conduit 32 which leads to the reservoir 11. The recessed central port 24 is in communication with the fluid chamber 40 by means of a fluid passage 33 formed in the housing 22 to connect with a conduit 34 passing through a frame member 50 to the fluid chamber 40. The spool valve 25 may be reciprocated so that the central land 26 will place the recessed central port 24 in communication with either the upper or lower fluid chambers 29 and 30, respectively. Hence, by reciprocating the spool valve 25, the fluid chamber 40 may be in communication with either the upper or lower chambers 29 and 30, respectively, and thereby be in fluid communication with the reservoir 11 or the pump 10. I

The spool valve 25 is cyclically reciprocated by a shaftdriven rotatable eccentric cam 35 which is positioned to engage the end land 28 extending through the open end of the cylindrical bore 23. The end land 28 is urged in engagement with the cam 35 by means of a compression spring 36 disposed within the cylindrical bore 23 to engage the closed end of the bore 23 and the end land 27 of the valve 25. The cam 35 is continuously rotated by any suitable means for synchronous rotation and thereby is effective to reciprocate the valve 25 within limits in a predetermined time relation.

The working fluid, which may be supplied under pressure by the pump and cyclically admitted to the fluid chamber 40 by the valve means 20, is permitted to flow from the chamber 40 through a series of spaced openings 41 in the chamber 40 connected with a series of spaced fluid passages 42 formed in a block element 43 fixed be tween the frame member 50 and a frame member 5 1. The fluid passages 42 connect with a series of spaced cylindrical bores 44 which extend from the passages 42 through the block element 43. A series of work elements, such as punch operators 45, are slidably disposed within the cylindrical bores 44. The punch operators 45, as will be described in greater detail later herein, are adapted to actuate a series of spaced punch elements 46.

Passage of the cyclically admitted fluid impulses from the fluid chamber 40 through the fluid passages 42 is controlled by means of a series of spaced flatfaced poppet valves 60. The valves 60 have an upper face 61 directed toward the fluid passages 42 and an opposite face 62. The face 61 is of suflicient diameter to cover the openings 41 of the chamber 46. Valve stems 63 on one end are fixedly attached to or integral with the face 62 of the valves 60. The valve stems 63 extend from within the fluid chamber 40 through a plate 64 fixed between the frame members 50 and 51. The plate 64 may be provided with a rectangular recess to form the chamber 40.

The portion of the plate 64 surrounding the recess is positioned to abut the block element 43. The conduit 34, which is connected to the fluid chamber 40, may either extend through the frame member 50 and the plate 64 or may connect witha bore 50a provided in the frame member 50 aligned with a bore 640 in the plate 64 extending to the chamber 40.

The extreme lower end of the valve stems 63 are fastened in a suit-able manner to a corresponding number of armatures 65 of magnets 66, as shown in greater detail in FIGS. 3a, 3b and 3c. The armatures 65 are biased by springs 67 in a manner that, when the magnets 66 are de-energized for more than one cycle of operation, the faces 61 of the valves 60 are held against the openings 41 in the chamber 40 communicating with the fluid passages 42. However, when the magnets are de-energized after having been energized, as in FIG. 3a, the face 61 of the Valves 60 are in close proximity to the openings 41 and the fluid impulse entering the chamber 40 will act upon the valves 60 in this position to move the same to a position where the face 61 seals off the related opening 41. The phenomena involved in this action is that, with the face 61 of the valves 60 in close proximity to the openings 41, the fluid pressure across the face 61 is much less than the fluid pressure on the face 62, as shown in FIG. 3d. In FIG. 3d the magnitude of pressure is represented by the length of the arrows. Hence, even through the effective area upon which the fluid pressure may act is less for the face 62 than for the face 61, due to the lower pressure on acting upon the face 61 than on face 62, the resultant forces cause the valves 60 to move upward to seal off the openings 41. While a small amount of fluid will pass through the openings 41 before the same are sealed off by the valves 60, this leakage fluid is insuflicient to displace the punch operators 45. The fluid which passes as leakage may drain back to the reservoir 11 by drain conduits 43a, FIG. 1. Also, the mass of the punch operators 45 is greater than the mass of the valves 60. Hence the valves 60 move prior to any movement of the punch operators 45. In fact, the valves 60 will be moved to the closed position before there will be any movement of the punch operators 45. Of course, once the valves 60 are closed, fluid under pressure cannot pass to act upon the punch operators.

However, when the magnets 66 are energized, the face 61 of the valves 60 are moved out of close proximity to the openings 41, as in FIG. 3b. Under this condition,

when fluid under pressure enters the fluid chamber 40, the fluid pressure upon the face 61 is substantially equal to that upon the face 62, as shown in FIG. 30 the length of the arrows indicating magnitude of pressure. Since the effective area of the face 61 is greater than the effective area of the face 62, as represented by the greater number of arrows, because of the area occupied by the valve stem 63, the valves 60 biased toward the open position are forced by the fluid pressure downward away from the openings 41 to their fully opened position, as shown in FIG. 30. With the valves in their fully opened position, the fluid may flow from the chamber 40 through the openings 41 and fluid passages 42 to act upon the punch operators 45. Again, since the mass of the punch operators 45 is greater than the mass of the valves 60, the valves 60 move first and very rapidly to the open position.

Thus, it is seen that the working fluid impulses under pressure are utilized to open and close the valves 60 for controlling the flow of the fluid from the fluid chamber 40. The valves 60 are merely biased toward an open or closed position upon entry of the fluid under pressure into the chamber. By this arrangement, it is possible to selectively control the flow of fluid under pressure from the chamber with the fluid impulses entering the chamber at very high cyclic rates.

The fluid impulses enter the chamber 40 under pressure when the spool valve '25, FIG. 1 is shifted upward by the eccentric cam 35 so that the central land 26 is positioned to cut off communication of the central port 24 with the upper chamber 29 and establish communication of the central port 24 with the lower chamber 30. Under these conditions, the fluid will pass from the chamber 30 to the chamber 40 and through the openings 41, which are not sealed ofl:' by the valves 60 or those openings 41 associated with the magnets 66 that are energized.

Since fluid under pressure is cyclically admitted to the fluid chamber '40, the magnets 66 may be selectively energized prior to the entry of the fluid into the chamber. Of course, fluid flows from the chamber 40 to the reservoir 11 when the spool valve 25 is shifted by the eccentric cam 35 to place the upper chamber 29 in communication with the central port 24, the lower chamber 30 being cut off therefrom.

Successful operation has been achieved at speeds of approximately 7800 cycles per minute at pressures between 800 and 1000 psi. The displacement of the valve 60 to the fully opened position, for purposes of example, approximately .006 inch. When the valve 60 is biased toward the open position, it is approximately .004 inch away from the opening 41. When biased toward the closed position, the valve 60 is approximately .002 inch away from opening 41 at the time the fluid impulse is admitted to the fluid chamber. It should be noted that the speed of operation, the pressure of the fluid, and the poppet valve movement may be varied without departing from the spirit of the invention.

The present invention finds great utility for high-speed punching operations wherein perforations are selectively entered in coded form in record cards to represent data. The perforations may subsequently be sensed to permit accumulation of data and other like type of operations;

For purposes of example, the invention has been embodied in a record card punching machine, as shown in FIGS. 1, 2 and 4. While it would be possible to employ a single row of punches for perforating the index positions of a record card as the same is advanced rowby row relative to the punches, four rows of punches are utilized in this example, as in FIGS. 2 and 4. Each row contains 40 punches; the punches in two adjacent rows of the four rows are identically spaced and offset from the punches in the other two adjacent rows so as to facilitate the punching of any of the eighty columns of the record card in two adjacent rows as the record card is positioned in succession relative to the four rows of punches two rows at a time.

The magnets 66 for operating the valves 60 are arranged in a steplike fashion about the longitudinal center of the four rows of punches, as in FIG. 2; only two rows of magnets are shown. The valve stems 63 for the inner rows of punches are longer than the valve stems for the center rows to permit the desired arrangement of the magnets.

The electrical impulses for energizing the magnets 66 may emanate from a card reader which may be separate from or integral with the punching machine. The card reader may have the facility of sensing perforations in record cards to generate a succession of electrical impulses Which are then applied to certain selected magnets 66 to effect selective punching in blank record cards fed relative to the punches.

The general schematic arrangement of the punching machine is shown in FIG. 4. Blank record cards 80 contained in a hopper or magazine, not shown, are advanced in seriatim by a conventional picker knife 81, operated in the conventional manner, to a pair of cooperating feed rolls 82. The feed rolls 82 are driven from an intermittent hydraulic drive 83 shown schematically, through a gear train 84. The intermittent hydraulic drive may be of the type described in the application of S. T. Titcomb, Serial No. 698,840, filed November 25, 1959, issued as Patent No. 2,938,501. As the blank cards 80 are fed by the feed rolls 82, they pass between conventional sensing brushes 86 and contact roll 87 to a pair of cooperating feed rolls 88, which are also driven from the intermittent hydraulic drive 83. By means of the hydraulic drive 83, the feed rolls 88 feed the blank record cards 80 in successive increments at high speed into punching position relative to the punches 46.

The cards 80 advance from the feed rolls 88 to a pair of feed rolls 89, also driven from the intermittent hydraulic drive 83. The feed rolls 89 feed the cards 80 between sensing brushes 91 and contact roll 92 to cooperating feed rolls 93 which feed the cards to a card stacker, not shown, to form a stack of punched cards 94.

As the blank cards 80, FIG. 4, are fed relative to the punches 46, the magnets 66 for controlling the movement of the control valves 60 are selectively energized. The impulses for selectively energizing the magnets 66 may come from a card reader or from the results of analyzing a pattern card leading the group of blank cards 80, as described in the patent to C. D. Lake, No. 2,032,805. The perforations in the pattern card are analyzed by the brushes 91, thereby permitting the closing of a circuit diagrammatically shown for one order, as from line L, contact roll 92, through brush 91, conductor 96, magnet 66 to line L. When the brush 91 senses a perforation at an index position of the pattern card, the corresponding index position of the following blank card 80 is over the punch 46; and, as a result of energization of the magnet 66 and the operation of the hydraulic punch operator 45, the blank card 80 is perforated by the punch 46. After the first blank card is perforated, it may act as a pattern card for the following blank card of the group, as is well known in this form of card punching machine.

Once punching takes place, it is necessary to restore the punches 46 and the punch operator 45 to enable a subsequent punching operation. The punches 46 which, in effect, restore the punch operators 45 are restored by means of a cyclically operated punch restore bail 100, FIGS. 1 and 2, common to all of the punches 46 and operated in synchronism with the operation of the punches.

The punch restore bail 11 is essentially a rectangular plate 101 having end portions 102 carried between lands 103 and 104 of slidable pistons 106. The rectangular plate 101 is provided with four equally spaced longitudinal slots 107, FIG. 2, extending intermediate of the end portions 102 to form lands or rails 108. The rails 108 lie well into notches 46a formed in the punches 46. The notches 46a are of suflicient length to permit the bail to occupy a restore position while punching takes place. After punching, the bail is operated to move the punches 46 to their restore position, and then the bail 100 is returned to its restore position. Thus, punching always takes place with the bail 100 in its restore position. Further, this arrangement permits the bail 100 to be operated at a high cyclic rate in synchronisrn with the operation of the punches.

The bail 100 is moved from its restore position to a position to restore the punches 46 and back to its restore position by the pistons 106. The lands 103, FIGS. 1 and 2, of the pistons 106 are slidable in bores 4312 provided in the block element 43, while the lands 104 are slidable in bores 109 formed in punch element guide block 111. The pistons 106 are actuated by fluid impulses admitted to the bores 43b and 109 from valve means 112, FIG. 1.

Fluid under pressure is supplied to the valve means 112 by a fluid pressure generating means or pump 113, also driven by the motor M. The pump 113 withdraws fluid from the reservoir 11 through a suction conduit 114 to deliver fluid under pressure to a conduit 116 which is connected to a fluid conducting passage 117 formed in a cored housing 118 of the valve means 112. The conduit 116 also interconnects in series check valve 119, fiiter 121, pressure regulator 122, and accumulator 123 disposed between the pump 113 and the cored housing 118.

The housing 118 is provided with a cylindrical bore 124 open at one end and closed at the other and having a recessed central port 126 and recessed end ports 127 and 128. A spool valve 129, received by the bore 124, includes a central land 131 disposed between spaced end lands 132 and 133 which are adapted to conrol fluid flow through the related ports 126, 127 and 128, respectively. Additionally, the lands of the spool valve 129 lie within the cylindrical bore 124 to provide upper and lower fluid conducting chambers 134 and 136, respectively, disposed on opposite sides of the central land 131.

As shown, the central port 126 is in fluid communication with the pump 113 by the fluid conduit 116 and the fluid conducting passage 117. The recessed ports 127 and 128 are in fluid communication with the reservoir 11 by means of a fluid conduit 137 connected with fluid conducting passages 138 and 139 formed in the housing 118 to connect with the recessed ports 127 and 128, respectively.

tFllJld impulses may flow from the fluid conducting chamber 136 by means of a fluid conduit 141 connected to a fluid conducting passage 142 formed in the housing 118 to connect with the fluid conducting chamber 136. The conduit 141 is connected to fluid passages 143 and 144 formed in the frame members 50 and 51, respectively. The passages 143 and 144 extend through the block element 43 to connect with the bores 43b.

A fluid conducting passage 146 formed in the housing 118 to connect with the fluid conducting chamber 134 also connects with a fluid conduit 147. The fluid conduit 147 is connected with fluid passages 148 and 149 formed in the frame members 50 and 51, respectively. The fluid passages 148 and 149 extend into the punch guide block 111 to connect with the cylindrical bores 109.

Fluid under pressure is alternately supplied to the bores 43a and 109 by reciprocating the valve 129. As the valve 129 reciprocates, the central port 126 and end ports 127 and 128 are alternately admitted to and prevented from fluid communication with the adjacent fluid conducting chambers 134 and 136, respectively. Hence, the conduits 141 and 147 connecting with the fluid conducting chambers 134 and 136 are alternately in fluid communication with the pump 113 and reservoir 11.

The spool valve 129 is cyclically reciprocated by a shaft-driven rotatable eccentric cam 151 which is positioned to engage the end land 132 extending through the open end of the cylindrical bore 124. The end land 132 is urged in engagement with the cam 151 by means of a compression spring 152 disposed within the cylindrical bore 124 to engage the closed end of the bore 124 and the end land 133 of the valve 129. The cam 152 is rotated by any suitable means for synchronous rotation and is thereby eflective to reciprocate the valve 129 within limits in a predetermined time relation relative to the shifting of the valve '25.

Thus, it is seen that the punch restore bail 100 will be moved from the restore position, the position shown in FIG. '1, downwardly as fluid under pressure enters the bores 109 to act upon the lands 104 of the pistons 1106. The bores 43b at this time are in fluid communication with the reservoir 11. Subsequently, the punch restore bail is moved upwardly to the restore position when fluid under pressure is applied to the cylindrical bores 43b, whereby the fluid under pressure acts upon the lands 103 of the pistons 106 to displace the same upwardly within the bores 43b. The bores 109 at this time are in fluid communication with the reservoir 11. As the bail moves downwardly from its restore position, the punches 46 and the punch operators 45 are restored. As the punch operators restore, fluid is forced from the bores 44 through the passages 42 and into the chamber 40, which is at this time in fluid communication with the reservoir. The punch restore bail 100 then moves upwardly to its restore position.

In order to understand the time relationship between the reciprocation of the valve 129 and the valve 25, reference is made to the diagram shown in FIG. 5.

The entire punching cycle, which includes time for transporting the record card into punching position, is approximately 8.57 milliseconds. However, punching takes place in approximately four milliseconds.

Assuming that the record card is being transported into punching position starting at of a machine subcycle, the record card arrives at the punching position at approximately 192, as represented by curve A. While the record card is being transported, the valve 129 is, first, in approximately the position shown in FIG. 1 and fluid under pressure had entered the bores 109 to act upon the lands 104 and thereby displaced the pistons 106 and carried the punch restore bail 100 downward so that the punches 46 are in the restore position. At approximately 62, FIGS. 1 and 5, the valve 129 is shifted upward, whereby fluid under pressure is permitted to enter the bores 43b to act upon the lands 103 and displace the pistons 106 upward to move the punch restore bail 100 to its restore position. The bail 100 arrives in the restore position at approximately 156 and remains in this position until approximately 256. At 256 the valve 129 is again shifted to permit fluid under pressure to act upon the lands 104 to shift the pistons 106 downward and thereby move the bail 100 to restore the punches 46. The bail 100 completely restores the punches at approximately 350 and remains in the punch restore position until approximately 62 of the succeeding machine subcycle. The action of the punch restore bail 100, as just described, is represented by curve B in FIG. 5. The important thing to note, as will be seen shortly, is that the punch restore bail 100 is in its restore position and the punches have been restored by the time punching is to take place.

Of course, when the valve 129 was shifted in the manner described, the cylindrical bore not receiving fluid under pressure was in fluid communication with the reservoir 11.

The valve 25, FIGS. 1 and 5, is in its fully downward position to place the fluid chamber 40 in fluid communication with the reservoir 11 from approximately 292 to 156. At 156 the eccentric cam 35 acts to shift the valve 25 upward; however, the chamber 40 remains in fluid communication with the reservoir until approximately 192, at which time the central land 26 has instantaneously sealed its related port 24 from fluid communication with both of the fluid chambers 29 and 30. Continued upward movement of the valve 25 permits fluid under pressure to enter the chamber 40. The chamber 40 is in fluid communication with the pump 10 from approximately 192 to 256; at 256 the valve 25 has shifted downward so that the land 26 again seals oh. the related port 24 from fluid communication with the charm hers 29 and 30. Further downward movement of the valve 25 again places the chamber 40 in fluid communication with the reservoir 11, The action of the valve 25 just described is represented by curve D in FIG. 5.

While fluid under pressure is cyclically admitted to the chamber 40 during 192 to 256 of a machine subcycle, punching will take place only if the magnets 66 are energized. In the event one of the punches 46 is to be operated to enter a perforation in the record card at a selected index position, the magnet 66 associated with the poppet valve 60 for controlling the passage of fluid from the chamber 40 to act upon the punch operator 45 for actuating the punch 46 is energized at approximately 292 of one machine subcycle and remains energized until approximately 256 of the following machine subcycle. Energization of the magnet is represented by the line E in FIG. 5. As the magnet 66 is ener-r gized, the poppet valve 60 is displaced downwardly to uncover the related opening 41.

As fluid under pressure enters the fluid chamber 40 at approximately 192, the magnet 66 has caused the valve 60 to be displaced approximately .004 inch away from the opening 41. The fluid under pressure acts upon the displaced valve 60 to move the same to its fully opened position. With the valve 60 open, the fluid under pressure passes through the opening 41 and the fluid passage 42 to act upon the punch operator 45. The fluid under pressure displaces the punch operator upwardly. The upward movement of the punch operator 45 carries the associated punch 46 upwardly to perforate the record card. The movement of the poppet valve 60 under the influence of the magnet 66 and the fluid under pressure in the chamber 40 is represented by the curve F while movement of the punch 46 is represented by the curve G, FIG. 5. In examining curve F, it is seen that at 0 the valve 60 is already moving away from the opening 41 because the magnet 66 had been energized at 292 of the previous machine subcycle. The valve continues to open at a rather slow rate until 192, at which time the valve 60 is rapidly moved to its fully opened position by the fluid under pressure in the chamber 40. The valve 60 stays in the fully opened position until 256, at which time the magnet 66 becomes de-energized. However, from 256 to 292, the period during which the magnet 66 is de-energized for all instances, the valve 60 is still shown in the fully opened position. The reason for this is that, although the magnet 66 is de-energized, the punch restore bail is restoring the punches and thereby moves the punch operator 45 which displaces fluid from the bore 44 and the passage 42. The displaced fluid acts upon the valve 60 to hold it open until approximately 350. Hence, if the magnet 66 is again energized at 292, as shown by the curve E, the valve 60 will remain open, as shown by the curve F.

Looking at curve G, it is seen that the punch 46 starts moving upwardly as fluid under pressure leaves the fluid chamber 40. The punch 46 continues moving upwardly until it reaches its fully extended position, which may be determined by a stop member or the bail 100. The punch 46 then remains in the extended position until the punch restore bail 100 moves the punch downward at 256. The punch 46 is fully restored at 350.

In the event the magnet 66 was not energized again at 292, the valve 60 would start moving toward the closed position at approximately 350", as shown by dashed curve H. The valve 60 would continue in moving toward the closed position during the next machine sub- 11 cycle, as represented by the curve I; and, at 192 of that machine subcycle, the valve 60 would be approximately .002 inch away from the opening 41 at the time fluid under pressure enters the chamber 40 to act upon the valve 60 to move the same to its closed position. Under these conditions, the fluid under pressure cannot pass from the chamber 40 to displace the punch operator 45. Hence, the punch 46 will not be actuated to effect a perforation in the record card.

Since the punch 46 is not displaced when th valve 68 is closed, the valve 60 is not opened as the punch restore bail 100 goes through its cyclic movement to restore the punch 46. Hence, the valve 60 remains closed during the period from 256 to 292, as shown by the curve I. Further, assuming the magnet 66 is not energized at 292, the valve 60 still remains closed, as represented by curve I.

The curves I, F and H represent the four types of conditions which may exist with respect to the poppet valves 60; namely, the magnet 66 energized after not being energized in the preceding machine subcycle, the magnet 66 energized after having been energized in the previous machine subcycle, the magnet 66 de-energized after having been energized, and the magnet 66 de-energized after not having been energized in the previous machine subcycle.

From the above, it is seen that apparatus has been provided to control the passage of fluid impulses from a fluid chamber where the fluid impulse acts upon the control means to move the same to the open or closed position depending upon the particular position of the control means at the time of entry of the fluid impulse to the fluid chamber. Further, it is seen that the apparatus for controlling the passage of fluid impulses from a fluid chamber has been incorporated in a machine for perforating record cards at selected index positions. The fluid impulse is selectively permitted to pass from a fluid chamber to act upon a punch operator which actuates a punch member for perforating the record cards. After punching takes place, a hydraulically operated member restores the punch and punch operator to permit a subsequent punching operation.

While there have been shown and described and pointed out the fundamental novel features of the invention as applied to a preferred embodiment, it will be understood that various omissions and substitutions and changes in the form and details of the device illustrated and in its operation may be made by those skilled in the art, without departing from the spirit of the invention. It is the intention, therefore, to be limited only as indicated by the scope of the following claims.

What is claimed is:

1. In a cyclically operable punching machine for entering perforations into record cards at selected index positions, a reciprocative punch element; a hydraulically actuated punch operator for said punch; a fluid conductor for transmitting fluid impulses to said punch opera-tor; a fluid chamber having an outlet connected to communicate with said fluid condutor; a valve having first and second faces disposed within said fluid chamber so that said first face is directed toward said outlet and adapted to be movable toward and away from the outlet to control the passage of fluid from the outlet to said fluid conductor; a valve stem connected to said second face of said valve to extend away therefrom and through said fluid chamber; a magnet having an armature connected to said valve stem; means for normally biasing said armature in a position to hold the first face of said valve against said outlet; means for cyclically applying fluid impulses to said fluid chamber; and means for selectively energizing and de-energizing said magnet prior to the application of a fluid impulse to move the valve out of and into close proximity to said outlet, whereupon application of a fluid impulse acts upon said first and second faces of said valve to move the same further away from and toward said outlet, respectively,

to permit and prevent fluid under pressure to pass through said outlet.

2. In a cyclically operable punching machine for entering perforations into record cards at selected index positions, a series of reciprocative punch elements adapted for perforating a plurality of index positions at selected cycle points; a series of hydraulically actuated punch operators, one for each punch; a series of fluid conductors connected to transmit fluid impulses to each punch operator; a fluid chamber having a series of outlets connected to said fluid conductors; a series of valves each having first and second faces disposed in said chamber so that said first faces are directed toward said outlets and adapted to be movable toward and away from said outlets to control the passage of fluid from the outlets to the related fluid conductors; valve stems connected to said second faces of said valves to extend away therefrom and through said fluid chamber; a series of magnets having armatures connected to said valve stems; means for normally biasing said armatures to hold said first faces of said valves against said outlets; means for cyclically applying fluid impulses to said chamber; and means for selectively energizing and de-energizing said magnets prior to the application of a fluid impulse to said chamber to move the related valves out of and into close proximity to said outlets, respectively, whereupon application of a fluid impulse acts upon said first and second faces of those valves out of close proximity of the related openings to move these valves further away from said outlets and pass therethrough to actuate the related punch operators and thereby reciprocate the related punches to effect perforations at a plurality of selected index positions, those valves in close proximity to said openings are moved against said openings by said fluid impulse.

3. Hydraulic apparatus for selectively controlling the transmission of fluid impulses comprising: a fluid chamber having inlet and outlet openings for ingress and egress of fluid impulses; a flatfaced valve having first and second faces disposed within said fluid chamber so that said first faces are directed toward said outlet and movable to cover and uncover said outlet opening; a valve stem extending into said fluid chamber and attached to said second face of said valve; a magnet having an armature connected to said valve stem; biasing means for normally biasing said armature to hold said first face of said valve against said outlet opening; means for energizing and de-energizing said magnet to move the valve out of and into close proximity to said outlet opening; and means for admitting fluid impulses through said inlet whereby said fluid impulses act upon said first and second faces of said valve to move the same, said valve is moved to cover the outlet opening, if the magnet is de-energized, and moved further away from said outlet opening, if the magnet is energized.

4. Hydraulic apparatus for selectively controlling the transmission of fluid impulses comprising: a fluid chamber having an inlet and a plurality of outlets; a plurality of fluid conductors connected with said outlets; a plurality of cylindrical bores connected to communicate with said conductors; a plurality of pistons freely disposed in said cylindrical bores; a plurality of flatfaced valves each having first and second faces disposed to control the passage of fluid through said outlets; a plurality of valve stems connected to said second faces of said plurality of valves, said valve stems extending through said fluid chamber; a plurality of magnets having annatures connected to said valve stems; biasing means for normally biasing said armatures in a position to hold said first faces of said valves against said outlets; means for selectively energizing and de-energizing said magnets; and means for applying fluid impulses to the inlet opening of said chamber after selective energization and de-energization of said magnets whereby said fluid impulses act upon said first and second faces of said valves to move the same, the valves associated with the de-energized magnets are moved to seal off the related outlets and the valves associated with the 13 energized magnets are moved away from the related outlets so that the fluid impulses are permitted to pass through the related fluid conductors to act upon the pistons in said cylindrical bores.

5. In an arrangement of hydraulic apparatus for selectively controlling the passage of fluid impulses, a fluid chamber having an inlet and an outlet; means for cyclically admitting fluid impulses to said chamber through the inlet thereof; valve mechanism having an open and closed position situated'in said fluid chamber to control the passage of fluid through the outlet thereof, said valve mechanism having a. greater fluid pressure acting area directed toward said outlet than the fluid pressure acting area thereof directed toward said inlet; and magnetic means for selectively biasing said valve mechanism toward the open and closed positions, whereupon the fluid impulse entering the fluid chamber acts on said fluid pressure acting areas of said valve mechanism to move the same to the open and closed positions depending upon the biased position of the valve at the time of entry of said fluid impulse.

6. In an arrangement of hydraulic apparatus for selectively controlling the passage of fluid impulses from a fluid chamber having a single inlet and a plurality of outlets connected to a corresponding number of fluid conductors, the combination comprising: means for cyclically admitting fluid impulses to said fluid chamber through the inlet thereof; a plurality of valve mechanisms, each having an open and closed position, situated in said chamber to selectively control the passage of fluid from the chamber to the fluid conductors through the related outlets said plurality of valve mechanisms each having first and second faces with the first faces directed toward said related outlets, the fluid pressure acting area of said first faces being greater than that of said second faces; and a plurality of magnetic means for selectively biasing said plurality of valve mechanisms toward the open and closed positions, whereupon the fluid impulse acts upon said first and second faces to close those valve mechanisms biased toward the closed position and open those valve mechanisms biased toward the open position.

7. Apparatus of the type described comprising: a fluid chamber having an inlet and outlet, means for cyclically admitting fluid under pressure into said chamber through the inlet thereof, a poppet valve having first and second faces, the first face having a greater fluid pressure acting area than said second face, said first face being directed toward said outlet disposed in said chamber to be movable toward and away from said outlet to control passage of fluid therethrough, and actuating means for selectively moving said poppet valve so that the same will be in a predetermined position at the time of admission of fluid under pressure into said chamber whereby the fluid impulse will further move said poppet valve in the same direction that the poppet valve was moved by said actuating means.

8. Apparatus of the type described comprising: generating means for generating a steady flow of fluid under pressure; fluid impulse means hydraulically connected to said generating means for converting a steady flow of fluid under pressure to a predetermined cyclic flow of fluid impulses; a fluid chamber having an inlet and an outlet, said inlet being connected to said fluid impulse means; a poppet valve having first and second faces, said first face having a greater fluid pressure acting area than said second face with the first face directed toward said outlet disposed in said chamber to be movable toward and away from said outlet to control the passage of fluid therethrough; and actuating means for selectively moving said poppet valve so that the same will be in a predetermined position at the time of admission of a fluid impulse into said chamber whereby the fluid impulse will further move said poppet valve in the same direction that the poppet valve was moved by said actuating means.

9. Apparatus of the type described comprising: a reciprocative punch element; a hydraulically actuated punch operator for said punch element; a fluid chamber having an inlet and an outlet, said outlet being connected to said punch operator; fluid generating means for generating a steady flow of fluid under pressure; fluid impulse means connected to said fluid generating means for converting a steady flow of fluid under pressure to a predetermined cyclic flow of fluid impulses; means connected to said fluid impulse means and said inlet for conducting said fluid impulses to said chamber; a poppet valve having first and second faces, said first face having a greater fluid pressure acting area than said second face, said first face being directed toward said outlet disposed in said chamber to be movable toward and away from said outlet to cover and uncover said outlet and thereby control passage of fluid impulses from the fluid chamber to the punch operator; a magnet having an armature connected to said poppet valve; means for normally biasing said armature in a position whereby said poppet valve covers said outlet; and means for selectively energizing and de-energizing said magnet to attract and release said armature whereby said poppet valve is moved to a predetermined position upon admission of a fluid impulse into said chamber.

10. Apparatus of the type described according to claim 9 further comprising: cyclically operable punch restoring means for returning said punch element to its unoperated position in a timed relationship with said fluid impulse means.

11. Apparatus of the type described comprising: fluid generating means for generating a steady flow of fluid under pressure; fluid impulse means hydraulically connected to said fluid generating means for converting a steady flow of fluid under pressure to predetermined cyclic flow of fluid impulses; a fluid chamber having an inlet and a plurality of outlets, said inlet being connected to said fluid impulse means; a plurality of poppet valves each having first and second faces, said first faces having a greater fluid pressure acting area than said second faces, said first faces being directed toward said plurality of outlets and disposed in said chamber to be movable toward and away from said outlets to cover and uncover the same and thereby control pass-age of fluid impulses therethrough; and a plurality of magnets having armatures connected to said poppet valves, said magnets adapted to be selectively energized and tie-energized to attract and release said armatures whereby said poppet valves are moved to a predetermined position upon admission of an impulse into said chamber.

References Cited in the file of this patent UNITED STATES PATENTS 

